Expansible chamber rotary fluid displacement device



1952 J. M. CLARK 2,582,413

EXPANSIBLE CHAMBER ROTARY FLUID DISPLACEMENT DEVICE Filed July 20, 19452 SHEETS-SHEET l Jan. 15, 1952 J. M. CLARK 2,582,413

EXPANSIBLE CHAMBER ROTARY FLUID DISPLACEMENT DEVICE Filed July 20, 1945v 2 SHEETSSHEET 2 Patented Jan. 15, 1952 OFFICE EXPANSIBLE CHAMBERROTARY FLUID DISPLACEMENT DEVICE James M. Clark, New York, N. Y.

Application July 20, 1945, Serial No. 606,067

The present invention relates to fluid displacement devices and isparticularly adapted to that type of rotary blower, pump, motor and thelike which depends for the variation in the capacity or volume of itscompartments upon the rotation of its elements about oblique axes.

Many devices have been proposed which operate upon the principle of twoor more elements rotating upon oblique or intersecting axes such thatthe Working faces progressively approach and recede from each other tovary the'volum-e of their compartments during the rotative cycle. Theserotary devices have had the inherent advantage over devices of thereciprocating type in that they do not involve sudden changes indirection with their accompanying inertia effects and the resultingobjectionable pulsating flow as well as the necessity of suitable valvemeans. Very few of these prior rotary devices have, however, met withgeneral and eflicient use, due primarily to a plurality of reasons suchas the development of relatively great friction, excessive stresses uponthe rotating elements due to centrifugal forces at elevated speeds, andthe necessity for sealing between fixed and moving parts. Otherdifficulties have resulted from th lack of simplicity of design due tothe inherent irregularity of the working chambers and the necessity ofproviding universal or other power transmitting means between theobliquely disposed or Wobbling elements of many of such devices.

These and other difliculties and objections have been largely overcome,and eliminated altogether, by the rotary type fluid displacement devicecomprising the present invention. This device consists essentially, inits simplest form, of two rigid elements journaled upon oblique axes forrotation within a fixed casing, the working faces of the rotatingelements having radially extending projections or corrugations to whichare attached a flexible diaphragm by means of which one rigid elementtransmits rotation to the other and which cooperates to form variablecapacity compartments between the projections into and from which thefluid is successively drawn and expelled.

In its simplest preferred form the fluid enters axially into a fixedpart-spherical element having its center at the intersection of theoblique axes and from which it passes outwardly in a radial directioninto the compartments as their working faces are receding and isdischarged in the same outwardly radial direction from the opposite endsof the compartments as their working faces approach at the opposite sideof the 23 Claims. (Cl. 103-127) rotational cycle. The displacement isboth positive due to the reduction in compartment volume and the suctionand discharge is materially augmented by the centrifugal forcesdeveloped by the rotation of the fluid masses which are dischargedtangentially from the device.

The improved design is such that th interior of the casing is alsopart-spherical, being concentric with the central element, whereby theradial dimensions of the rotating elements remain fixed and maintainrelatively close clearances between the outer face of the centralelement and the inner faces of the casing, which also co operate toprovide working faces for the rotating compartments. The central elementis suitably apertured to provide an inlet opening and the casing issuitably formed to provide a tangential discharge opening. The flexiblediaphragm attached to the conic elements forms therewith a universaljoint or flexible coupling and the degree of flexing is of suchrelatively small proportions that the fatigue requirements of thediaphragm material is greatly'reduced. The radial projections on eachrigid element are preferably staggered or complementary with respect tothe projections on the opposed element and are disposed at sufficientintervals as measured rotationally as to provide a plurality of radiallyextending compartments. 7

The present rotary displacement devices are also such that they requirea minimum of accurately finished surfaces in Contact with the rotatingparts and the clearances between the fixed and rotating parts remainuniform and constant during its operation. The relatively low pressuredifferential between adjacent compartments as compared to the overallpressure difference between the suction and discharge compartmentsreduces the sealing problem and leakage losses to a minimum. v

The present invention is not limited to the above described form but isadvantageously adapted to duplex or multiple devices arranged either inparallel for increased volume or in series for higher pressures. It hasalso been found advantageous in this connection to provide a single unitcomprising two rigid journaled elements with one or more floatingcorrugated rigid elements having intermediate flexibl units.

It is d ly a major object of the present invention to provide arelatively simple rotary displacement device in which positivcompression is augmented by centrifugal effects to attain a relativelyhigh degree of eificiency. It is a fur ther object to provide in adevice of this type a flexible bellows or diaphragm which serves in thedual capacity of a piston to vary the compartment volume and as aflexible coupling to transmit rotation from one rotary element toanother thereby saving the weight and expense of additional moving pantssuch as a universal joint or other torque transmitting means.

It is a further object to provide a rotary displacement device which isof relatively simple construction and operation and is readilyadaptpartments are relatively long and require sealing only at theirends at which the clearances are uniformly and continuously maintained.

A further object resides in a novel bellows compartment construction asa result of the bending action, and fatigue conditions to which thebellows elements are subjected are reduced to a minimum and anyblow-back or leakage between the ends of adjacent compartments is alsokept within reasonable limits due to the relatively low pressuredifferential prevailing from one compartment to the next.

It is a still further object to provide such a rotary device in whichthe rotating elements are relatively lightly stressed, are comparativelylight in weight and the friction between the fixed and rotating elementsis relatively small. A further object resides in a unique bellowscompartment shape having a relatively high ratio of its area to itsvolume, which readily lends itself to the dissipation of the heat ofcompression which may be developed at higher pressures.

Other objects and advantages of the present invention will becomeapparent to those skilled inthe art to which it pertains after readingand understanding the present specification and the attached drawings,forming a part hereof, in which:

Fig. 1 is an axial cross-sectional view of a preferred embodiment of myimproved rotary displacement, device;

Fig. 2 is aside elevational view of the rotating elementsof Fig. 1;

Fig. 3 is a transverse view of the device as taken along the. planeindicated by the lines 33.v of Fig. 1;

Fig. 4 is a side view of the central rotating element;

Fig. 5 is a detailed view of an attachment of the flexible diaphragm tothe adjacent rotating elements adjacent their tips;

Fig. 6 is a cross-sectional view of the attachment taken along the lines6-6 of Fig. 5; and

Fig. 7 is. a developed diagrammatic view of the flexible diaphragmelements prior to their attachment to the adjacent rigid elements.

Referring now to the cross-section in Fig. 1, taken together with theside view of the rotating elements in Fig. 2, it will be seen that thecasing it is split or divided transversely into the main casing half 10aand the secondary or suction half lfib. A rigid driving rotor H isrotatably disposed within the casing half Illa, its hub portion beingkeyed at 13, or otherwise suitably fixed, to the drive shaft I2 which isjournalled for rotation, from a suitable powersource, upon thehorizontal axis A-B. The rotor H, which will hereinafter be more fullydescribed, has a part-spherical concave face He which rotates about oraround a similar but convex partspherical outer face of a central inletelement i i which is fixed to the casing half lob. This central elementIt may be fully supported in a cantilever fashion from the casing halflllb, by the inlet hub element 18 and its outer end may be additionallysupported in an anti-friction bearing l5 having its outer race carriedby the hub of the rotor H, as shown in Fig. l.

The casing half. Illa is provided with a hub portion 10h within which amain anti-friction thrust bearing I6 is carried for the journalling ofthe drive-shaft l2. The latter is provided with an integral. headportion lZa which rotates within a recessed end portion of the centralelement M, and against the hub llh of the rotor ii. The inner races ofthe thrust bearing 16 are retained against the rotor hub Hh by means ofthe threaded locking ring i2b on the shaft it. The outer races of thebearing it are retained and positioned by the bearing cap ll fastened tothe casing hub- Hih by the attachment screws lla, the cap fittingpreferably being provided with a suitable gasket or lubricant seal.

The central inlet fitting i4 is rigidly supported from the casing halfIllb by the inlet hubfitting i8 which has a cylindrical portion 18bprojecting into a corresponding female hub portion Hid of the centralfitting to which it is fixed by the key 280. The fitting i8 is attachedto the casing hair Nib by means of suitable attachmentscrews lea and ispreferably provided with a tapped or threaded inlet hub IM to receive avsuction pipe or other fitting as desired. The inlet bore iS'b of thefitting 13, as well as the adjacent bore i i-b are preferably co-axialand continuous internally, having a common axis. CD. This axis isobliquely disposed with respect. to the horizontal axis AB andintersects the latter at the point 0, which will preferably be referredto as the geometrical center of the device and the point from which thebasic part-spherical surfaces and radial lines preferably originate, aswill hereinafter be more fully explained.

The central fitting l4 has a part-spherical outer surface We, the centerof which is the geometrical center point 0 and is internally bored suchthat it serves as an elbow to smoothly direct the axial flow enteringits bore Mb into a transverse and radially downward flow to the inletopening or port 54a through its part-spherical outer surface f le. Theouter surface of the hub portion l ib of the fitting it is suitablyshaped to receive the anti-friction bearing i9 against a shoulder formedadjacent its part-spherical portion Mo and is threaded to receive thebearing retainer ring its. The bearing i5 is disposed in a co-axial andnormal relationship with respect to the oblique axis C-OD. This bearingforms the rotatable support for the rigid driven rotor 29 whichisrotatable about the oblique axis CO and within a transverse planenormal thereto. Except icr its hub portion 2th, the rigid rotor 29: isidentical with and oppositely disposed with respect to the driving rotorll. Like its counterpart it has a part-spherical concave inner facev 230which ro tates about the similar but con-vex part-spherical outer face llo of the central element M, the major difference residing in its havinga larger internal opening to engage the larger diameter bearing l9 andpermit of the flu-id inlet lib-48b,

whereas the driving rotor has an inwardly extending hub portion toengage and be driven by the drive shaft I2.

I The driving rotor I I is preferably formed such that it presents aradially corrugated or sinusoidal-shaped working face toward the similarshaped driven rotor 20. The ridges or male projecting portions of thecorrugations are defined by the radial lines I la which, extendedinwardly, each pass through the center and define a relatively flat coneof revolution having its apex at the center 0. The valleys or femaleindentations of the corrugations are defined by the radial lines III)which, extended inwardly, each also pass through the center 0 and definea somewhat steeper cone of revolution, also having its apex at thecenter 0. The corrugated working face of the driving rotor I Iterminates outwardly at a convex part-spherical outer surface IId whichforms an outer flange backing up the corrugations and rotates closelycontiguous to a concave part-spherical portion Inc formed within thecasing portion Illa. In machines designed for higher pressures suitablesealing means may be provided at these contiguous surfaces to preventblow-back of fluid from the discharge portion, around and behind therotors II and 20, to the suction portion of the casing. The corrugationssimilarly extend inwardly where they terminate at the inner concavepart-spherical surface IIc, contiguous to the outer convex surfacev I40of the cen tral element I4.

The driven rotor is similarly formed such that it presents a radiallycorrugated working face having corresponding ridges 20a and valleys 20bterminating in a convex part-spherical outer surface 20d which forms anouter flange backing up the corrugations and rotates closely contiguousto the concave part-spherical portion Illa formed within the casingportion Illb. For illustrative purposes rotors II and 20 have been shownas having eight complete corrugations in each of their working faces,although efficient devices may be designed having lesser or greaternumbers of corrugations. These rotors should, however, each have a likenumber of corrugations and the corrugations of one should be staggeredor offset with respect to those of the opposite rotor; that is, theridges I la of rotor I I are opposite to the valleys 20b of rotor 20,and the ridges 20a of the latter rotor are in turn opposite the valleysI lb of rotor I I, as may be clearly seen in Fig. 2.

In the modification which has been illustrated in the drawings anintermediate or third rigid element 22 is provided between the drivingand driven rotors II and 20. This intermediate rotor need notnecessarily be perfectly rigid but may preferably be formed from a discof metal or other material of a thickness which permits of a slightdegree of flexing. It preferably is formed into a symmetrically conicelement with a like number of similar radial corrugations as provided inthe rotors II and 20. This intermediate corrugated rotor 22, which maypreferably be termed a floating rotor, is shown in detail in Fig. 4, andin its assembled relationship in the device in Figs. 1 and 2.

This rotor 22 may be made from an annular disc of flat sheet material ofsuch inner and outer diameters that when given its serrated orcorrugated form the inner periphery 220 of the corrugations forms aspherical inside diameter of sinusoidal configuration which permits itto be rotated contiguous to and with a relatively small of the outerworking face I40 of the fixed central inlet element I4. Similarly itsouter periphery 22d forms a virtual outside diameter which per mits itto be rotated with a relatively small clearance with respect to theinner working faces I00 and I07 of the fixed casing elements Illa andIBb. This floating disc 22 is preferably formed with corrugations oflike pitch, depth and configuration as those of the rigid driving anddriven discs or rotors II and 20 and each of its medians or radial lines22a should pass closely through its center of development 0, which isalso the geometrical center of each of the spherical or partsphericalsurfaces previously referred to. It will be obvious, of-course, thatwhere the disc 22 is made from a sheet of uniform thickness, as shown inthe drawings, the radial lines 22a when projected inwardly will pass thepoint 0 to within approximately one-half this thickness.

Between the driving rotor II and the floating disc 22 there is disposeda relatively flat flexible diaphragm 2|, and a like flexible diaphragm23 is disposed between the floating disc 22 and the driven rotor 20.These flexible diaphragms are preferably made of rubber or syntheticrubber, such as neoprene, Thiokol, rubberized fabric, or similarcompositions, or they may be of steel or other metal, or other flexiblematerial having suitable flexing, fatigue, corrosion-resistant and othercharacteristics as may be required by the specific fluid to be handledand the rotational speed, volume, pressure and other operatingconditions for which the particular device is designed.

Each flexible diaphragm 2| and 23 is formed into an annular disc offrusto-conical shape as shown in Fig. 7. They may be made of a singlecontinuouspiece or formed with a suitable joint. The inside diameter 2Idis preferably of the same order as the inside diameter as measuredthrough the center 0, of the part-spherical surfaces I I0 and 200 of therigid rotors II and 20, and that of the inner surfaces 220 of thefloating disc 22, being of such inside diameter that it may be rotatedand flexed contiguous to and with a relatively small clearance withrespect to the outer working face I40 of the central element I4.Similarly the outside diameter 0, 2Ic and 230 of the flexible elements2I and 23 is preferably of the same order as the corresponding diametersof the spherical outer surfaces IId, 20d and 22d of the driving, drivenand floating rotors, respectively.

Referring now to the assembly in Fig. 1, the driving rotor I0 isjournalled for rotation about the horizontal axis A--O-B and the drivenrotor is journalled for rotation about the inclined or oblique axisCO-D. The vertical line E-O-F is drawn normal to the horizontal axis AOBthrough the center 0- at which the horizontal and inclined axes alsointersect. The line G--OH represents a transverse plane, passing throughthe center 0, which plane is intermediate and equidistant from thehorizontal plane passing through C--D. The angle E-OG, as measured inthe vertical plane of the section in Fig. 1, is accordingly one half theangle C-OA; and angle C-O-G is equal to angle GO--B. Similarly the angleC-O--H is equal to the angle B-O--I-I. Since the angle C-O-B as measuredover the top of the device in Fig. 1 is appreciably less than the angleC-0-B as measured under the center 0, the rotors II and 2 0 haveapproached each other at the top forming aregion of maximum compression,and have mane receded from each other at the bottom to form a. region ofmaximum extension and suction.

The ridges Ila, asshown in Figs. and 6 are provided with a plurality ofradially aline'd tapped holes 24% which match similarly disposed holesvin the flexible diaphragm 2!, and the latter is attached along theiradjacent radial lines to the ridges Ila by means of the screws 25. Wherethe flexible diaphragm 2! isof metal or similar hard surfaced material,there is prefe'rab'ly provided an intermediate sealing strip 2? ofrubber or suitable gasket material. Similarly disposed holes areprovided in boththe dia-- phragm 2i, radially arranged intermediate thefirst said rows of holes, matching like holes in the floating disc 22,through which thelatter, a sealing strip El and the adjacent flexiblediaphragm 2i are attached as by the rivets 2%, or by bolts, or otherremovable attachment means. Where the flexible diaphragms 2i and 23 aremade of rubber or like material the sealing strips 2i may be dispensedwithyand washers or radially extending strips may be used under theheads of the fastening belts or rivets on the exposed side of eachdiapl-iragm.

Returning now to Figs; 1 and 3' both casing halves iiia and iilb areformed at their upper portions into a gradually increasing tangentialdischarge my preferably terminating in a threaded outlet Hid into whichmay be fitted a discharge pipe 3|. Each-casing half is also providedwith a peripheral flange iii) extending outwardly parallel to thetransverse plane defined by the intermediate line G-O--H; The flangeslei are interrupted above and below the discharge Mg and are aperturedcircumferentially as at 28 to receive the flange bolts 28 by which thehaives are bolted together preferably about an intermediate annulargasket to prevent passage of fluid therebetween, due either to sue tionor pressure created within the device. The casing portion Etais alsopreferably formed with a base or pedestal portion lie suitably aperturedfor bolting or fastening to a foundation or other supporting structure.

The operation of the' device is as feilows:

A suitable rotative source of power is preferably coupledto the driveshaft 52 to impart rotation thereto in the direction of the arrows inFigs. 1 and 3, or'in a" clockwise direction as viewed in Fig. 3. Thecasing halves and 5%, as well as the central inlet element Hi andh'ubfitting 18 attached to lilb, all remain" fixed. The rotating drive shafti2 imparts like rotation to the driving rotor it through the key 13'}and the rotor drives the flexible diaphragm 22-; the floating rotor 22,the flexible diaphragnrfi'ii and the driven rotor 26 each of which areconnected by the screws 25 and/orthe rivets 28: The

driving rotor ii is caused to rotate about the axis AO-B, the axis ofthe shaft 52; and the type inasmuch as it not only dispenseswith thenecessity for a universal joint or coupling, there by simplifying thedevice by serving adu'al pur pose, but alsocauses'therotating parts to"rotate uniformly" at the same angular velocity and is of a novelconstruction which permits the displaced fiuid to flow radiallyoutwardly through the coupling means, as will hereinafter be explained.

Let us now consider the compartment Ci, as indicated in Figs. 3 and i,which straddles the horizontal lateral axis K-OL. This compartment Ci,being intermediate the points of maximum approach of therotors H at 29at the top and of maximum divergence of these rotors at the bottom, isof average or mean capacity. The fluid iscon'fined within thiscompartment by the relatively flattened flexible diaphragm 2% on the oneside and the singlepitch of the corrugated floating disc'22 on the otherside. The leading andtrailin joints formed by the strips 2? at theradiallines of contact of the diaphragm 2i and the disc 22 prevent"leakage into the adjacentcompartments. The outside of the compartment Clis formed by the inner part-spherical surfaces 35c and iiij of thecasing halves 38c. and it?) against which the peripheral edges of theelements 2i and 22 rotate with a minimum clearance. The ner end of thecompartment Ci has just passed the point of inlet I as indicated in Fig.3 and defined by the point its and is open to the inlet port i ia in thefitting it and the iniet conduit 33.

its the chamber or compartment Ci is rotated, ale-chaise in Fig. throughsubstantially degrees into the position indicated at CA'its volume hasbeen materially increased. This increase is due to the flexiblediaphragm 2i being withdrawn away from the opposed disc 22 by virtue ofits attachment to the diverging rotor 2! by means of the screws 25. Thisincrease in volume of the space or compartment is accomplished byoutward flexing of the element 2! which may be of such resilientmaterial to stretch snificiently to permit slight circumferentialelongation between the lines of attachment to the floating disc which ispreferably rigid'or semi-rigidbut of such material as to permit slightbowing by virtue of its corrugated shape to contract siightly in thecircumferential direction to assist in the outward bulging or deflectionof the element ti. At this point itis fitting to note that the flexingand/or bowing of the elements i and 22 does not in any manner disturbtheir radial dimension or that ofthe defined compartment, this radialdimension remaining at all times equal to as indicated in Fig. 7. Thisfeature, which holds throughoutthe rotative cycle, derives the distinctadvantage .of maintaining the designed clearance between the inner andouter edges of the elements 23 and 22 and the part-spherical surfaces Weand" Ede-4th against which they rotate. Inasmuch as the vol'ume of thecoinpartment between Ci and C2 increases materially it is filled byfluiddrawn thereinto outwardly raflexing and bowing of the elements 2!and 22 until at Cit it is restored to its intermediate or mean volumesubstantially equivalent to that at Cl. Inasmuch as the compartment inrotatin from C2 to C3 is now confined by the spherical outer surface llo of the fitting- Mat its inner end the reduced volume is accompaniedby a material increase in pressure of the fluid confined therein.

At a point M in the rotative cycle which may be beyond the position C3the spherical inner surfaces lilo and lily of the casing halves arepreferably merged into the discharge portion log. This point has beenindicated as the beginning of the discharge in Fig. 3 as approximately2.2 degrees beyond the position C3 straddling the lateral axis KO-L butmay be appreciably more or less depending upon the nature of the fluid,gas or liquid to be handled by the device. As rotation of thecompartment continues to the upper position C4 the element 2! is flexedinto the position of maximum reversal, opposite its form at C2, due tothe maximum approach of the rotors II and 26 with respect to thefloating disc 22 which throughout the rotative cycle assumes afloatingly centralized position therebetween due to its attachment toeach through the resilient diaphragms 2! and 23. Accordingly as thecompartment is rotated from the point at which the casing discharge lllgdiverges outwardly from and slightly beyond the position C4 the furtherreduction in volume is accompanied by increased pressure and outwardtangential discharge of the fluid through the discharge Hlg, the outletltd and the conduit 3 l.

It will be noted that apart from the positive compression of the gas orliquid due to the varia .tion in volume or capacity of the severalcompartments that the fluid in entering axially and being rotated anddischarged outwardly has its compression appreciably augmented by thecentrifugal forces which are thus developed. The present device isaccordingly a combined rotary and centrifugal type compressor or pumpand its centrifugal effect assists materially in feeding the fluid intothe inner ends of the compartments and discharging the same from theirouter ends. For purposes of explanation the rotors H and 20 have beenshown as provided with eight projections and recesses apiece, or eightcomplete corrugations or sine curve face portions, and threeintermediate diaphragms or compartment forming discs have also beenshown.

It will be appreciated that successful devices utilizing the presentinvention may be made with rotors having a greater or lesser number ofprojections, having face portions of other shapes and with one or morecompartment forming discs. In the form of device illustrated there'areaccordingly formed sixteen pairs of laterally dis posed compartments ora total of thirty-two come partments, each of which has substantiallythe same volume at a given point in the rotative cycle. Each lateralpair will suck and discharge fluid simultaneously and at the sameinstant the leading and following pair of compartments will becompleting and starting their corresponding functions respectively dueto the overlapping of these compartments in the circumferentialdirection. This insures a relatively smooth dis{ charge flow free fromthe pulsations and surges common to many prior rotary devices.Accordingly there will be no tendency of blowback or leakage betweeneach laterally disposed pair and a relatively small tendency towardleakagebetween leading and trailing compartments, or vice v 'versa, dueto the pressure differential therebetween being but a small fraction ofthe pressure difference between the suction and discharge ports. Thissmall pressure diiferential also minimizes any tendency of the pressurewithin a given compartment affecting the shape of the adjacent leadingand trailing compartments.

It will also be noted that a very important feature of the presentdevice is the dual function of the elements 2!, 22 and 23 in bothdefining the compartments of compression and in serving as both aflexible anduniversal coupling to transmit rotative torque from thedriving rotor II to the driven rotor 2i). This is not only accomplishedin a flexible manner with the torque distributed uniformly along eachprojection of the 1 driven rotor but the rotors are driven uniformly atprecisely the same rotative speeds throughout the rotative cycle withoutthe whip or speed variation incidental to manv universal joints orcouplings as they rotate past their dead-center positions.

The embodiment shown is adapted for use as a blower, supercharger or aircompressor for the develop-ment of low or moderate pressures whenrotated at moderate speeds. It will be obvious to those skilled in theart that greater delivery and somewhat higher pressures may be obtainedfrom the illustrated device by rotation at higher speeds and acorresponding increase in input power. Higher pressures may be obtainedby designing the device with a greater obliquity of the rotor axes .A-Band C-D, or an increase in the angle COA. The latter angle may also bedecreased for lower pressures and when the angle COA is made to equalzero, or when the two rotor axes are aligned and the inlet port madeopen for a. full 360 degrees the device has been found to operatesuccessfully as a centrifugal type blower without positive action of thecompartments. A further modification of the invention contemplatescontrol means for varying the angle of obliquity CO--A to provide avariable capacity and pressure rotary displacement device. It will alsobe obvious to those skilled in the art that the described device may beadvantageously utilized as a pump for the displacement of water or otherfluids in which event it may be desirable to increase the angular extentof either or both the inlet and discharge portions of the cycle tocompensate for the lesser compressibility of the fluid and to otherwisemodify the arrangement and relationship of the component parts to mostefficiently handle the specific fluid for which the device is intended.

The present device is accordingly adapted to successful application inother forms than has been shown and described and such other forms whichvary either in general arrangement or the i details of the respectiveelements are all intended to come within the embrace of this inventionas more particularly defined in the appended claims.

I claim:

1. A rotary displacement device comprising a driving rotor, an opposeddriven rotor adapted for rotation on an axis inclined to the axis of thesaid driving rotor, radial projections on the opposed faces of saidrotors in a staggered re lationship with respect to each other, aflexible radially corrugated disc attached to the staggered projectionsof each said rotor defining radially extending compartments between saidrotors and means to conduct fluid into and from the ends 7 of saidcompartments.

2. A fluid displacement device comprising a circumferentially corrugateddriving rotor, a ciroumferentially corrugated driven rotor having theridges of its corrugations opposedly and complementarily disposed withrespect to those of said driving rotor, casing means for rotativelysupporting said rotors on inclined axes, fluid inlet and outlet meansformed by said casing means and flexible corrugated compartment formingmeans disposed between and attached to said ridges for rotativelycoupling the said rotors whereby said rotation causes reversible flexingof said compartment forming means and displacement of the fluid.

3. A fluid displacement device comprising a corrugated driving rotor, acorrugated driven rotor, the ridges of the said corrugations of bothsaid rotors opposedly disposed in a staggered relationship with respectto each other, casing means for rotatively supporting said rotors onintersecting axes, fluid inlet and outlet means formed by said casingmeans, flexible corrugated means attached to the ridges of saidcorrugations of each said rotor, said flexible means arranged to bothrotatively couple said rotors by attachment to said ridges and toprovide variable capacity compartments therebetween by the flexing ofsaid corrugated means.

4. A fluid displacement device comprising a driving rotor having radialprojections, a driven rotor having radial projections opposedly disposedin an offset relationship with respect to the projections of the firstsaid driving rotor, flexible sinusoidal bellows means attached to theprojections of each said rotor adapted to define a plurality of fluidchambers therebetween, a member adapted to rotationally support saidrotors on intersecting axes, inlet and outlet means formed by saidmember and means to rotate said driving rotor arranged to cause saidchambers to be varied in capacity by the reversible flexing of saidbellows means for the displacement of fluid from said inlet through saidoutlet means.

5. A rotary displacement device comprising a conic driving rotor, aconic driven rotor, said rotors formed with radially disposedprojections circumferentially offset with respect to each other, casingmeans for rotatively journaling said rotors on separate axes, fluidinlet and outlet means formed by said casing means, a plurality offlexible annularly shaped circumferentially deformed elements attachedto each other and to the projections of each said rotor adapted todefine a pluralit of radially extending fluid compression chamberstherebetween and means to rotate said rotors for the reversibledeformation of said elements and outward radial displacement of saidfluid.

6. A fluid compression device comprising a first rotor having radiallydisposed projections, a second rotor having radially disposedprojections opposedly facing the projections of said first rotor in acircumferentially staggered relationship therewith, a casing havingjournals for the 170- tational support of said rotors on oblique axes,fluid inlet and Outlet means formed by said casing, a plurality ofcircumferentially deformed flexible elements having radially disposedprolecting portions attached to each other and to the projections ofsaid rotors arranged. to define radially extending fluid chamberstherebetween and means to drive said rotors in such manner that fluid iscompressed within said fluid chank bers by the reverse flexing of saidflexible ele- 12 ments by the approaching and receding movements of therespective rotor projections.

7. A rotary fluid displacement device comprising a pair offrusto-conical rotors having radially disposed projections thereon, ahousing mem ber adapted to rotationally support said rotors for rotationabout intersecting axes with the frusto-conical surfaces and radialprojections of said rotors extending through the intersection of saidaxes, a hollow part-spherical inlet member disposed about said axesintersection arranged to supply fluid axially toward said intersectionand radially outwardly therefrom into the region between said rotors,fluid outlet means formed by said housing member, the said radialprojections of one rotor staggered with respect to the other rotor, andcircumferentially continuous corrugated diaphragm means of flexiblematerial fixedly attached to the projections of said rotors arranged todefine radially extending variable capacity compartments therebetweenintermittently in communication at their inner ends with said fluidinlet as said rotors are convergingly and divergingly rotated about saidintersecting axes for displacement of the fluid from the outer ends ofsaid compartments.

8. A rotary displacement device comprising a pair of conic rotors havingradially disposed projections, a housing having journals within whichjournals said rotors are adapted for rotation on intersecting axes,fluid inlet and outlet means formed by said housing, the saidprojections of said rotors radially arranged to extend through. theintersection of said axes and a flexible circumferentially corrugateddiaphagm having radial projections on its opposite sides alternatelyattached to the projections of said rotors arranged to define radiallyextending fluid spaces between said rotors and within said housing.

9. A rotary displacement device comprising a housing, a pair offrusto-conical circumferentially corrugated rotors journaled forrotation within said housing on intersecting axes, an inlet centrallydisposed about the said axes intersection carried by said housingarranged to supply fluid axially inward into said housing and radiallyoutward between said rotors, an outlet within said housing tangentiallydisposed with respect to the outer peripheries of said rotors carried bysaid housing, circumferentially corrugated flexible means disposedbetween and connected to the corrugations of said rotors definingradially extending fluid spaces successively open to the corrugations ofsaid inlet and outlet and to drive said rotors and said flexible meansfor the outward displacement of fluid from said housing.

10. In a rotary displacement device including a housing, a pair ofcircumferentially deformed irustoeconical rotors journal-ed for rotationwithin said housing on intersecting axes, said housing defining an axialinlet and a peripheral outlet, and a floating circumferentially deformeddisc disposed intermediate said rotors, flexible dia phragms attachedbetween said floating disc and each Said rotor in such manner that theyare circumferentially deformed to define a plurality of variablecapacity fluid compartments between said rotors in communication attheir inner ends with said inlet and at their outer ends with saidoutlet ll, The combination with a rotary displacemeet de ice comp isingafixed housin a pair of circumierentially corrugated conic rotors, andjournals carried by said. housing arranged for the rotation of saidrotors on separate but intersecting axes, of flexible corrugated meansdisposed between and interconnecting said rotors to form displacementcompartments in cooperation Wlth said rotors.

12. The combination with a rotary fluid displacement device comprisingaflxed housing, and a pair of frusto-conical circumferentiallycorrugated rotors adapted for rotation within said housing upon separateintersecting axes, of circumferentially continuous torque transmittingmeans of flexible material connecting said rotors arranged to definetherewith and with said housing circumferentially corrugatedcompartments having reversely bowing sides for the displacement offluid.

13. The combination with a rotary fluid displacement device comprisingcircumferentially deformed conic rotors arranged to rotate upon obliqueintersecting axes, the said rotor deformations being opposedly disposedin a circumferentially staggered relationship, and a continuous flexiblecircumferentially deformed fluid space defining means of flexiblematerial rotatively coupling said rotors and reversingly bowed by therotation of said rotors for the displacement of fluid therefrom.

14. A rotary fluid displacement device comprising a casing memberdefining a part-spherical chamber, a pair of circumferentially deformedconic rotors journaled within said casing member on separateintersecting axes, inlet and outlet means formed by said casing member,the said rotor deformations being opposedly disposed in acircumferentially staggered relationship, continuous circumferentiallydeformed diaphragm means of flexible material rotatively coupling saidrotors, said rotors and said diaphragm means having part-sphericalperipheries adapted to be rotated contiguous to said part-sphericalchamber, and means to rotate said rotors and said diaphragm means forthe reversible flexing of said means and the displacement of fluid fromwithin said casing.

15. A fluid displacement device including a fixed casing having aninternal chamber, a pair of rotors journaled in said casing for rotationon separate oblique axes, fluid inlet and outlet means carried by saidcasing said rotors having circumferentially deformed working faces,circumierentially deformed rigid diaphragm means disposed between saidrotors and flexible diaphragm means connecting the working faces of saidrotors with said rigid diaphragm means adapted to define fluidcompartments within said chamber and means to rotate said rotors for thevariable deformation of said compartments and the displacement of fluidfrom said chamber.

16. A fluid displacement device including a fixed casing having aninternal chamber, a pair of circumferentially deformed rotors journaledin said casing for rotation within said casing on intersecting axes,said casing having a tangential discharge portion, a fixed membercentrally disposed about said intersecting axes having a radial inletportion, circumferentially deformed means coupling said rotors definingradially extending fluid compartments successively opening at theirinner ends to said inlet portion, said coupling means formed from aninitially annular disc of flexible material and means to rotate one ofsaid rotors to deform said compartments for the displacement of fluidradially outward therethrough from said inlet to said discharge portion.

' 17. In a rotary displacement device comprising a radially ridged conicdriving rotor and aradial- 1y ridged conic driven rotor rotatable on anaxis intersecting that of said first rotor the said ra dial ridges beingopposedly disposed on the work faces of said rotors in acircumferentially staggered relationship, a flexible circumferentiallyand continuously bowed diaphragm intermediately connecting the ridges ofsaid rotors defining compartments therebetween, means to drive the firstof said rotors whereby said diaphragm is reversingly bowed towardand'away from the work face of one'of said rotors as it is rotated andmeans to conduct fluid into and from said compartments.

18. In a rotary displacement device comprising a corrugated faceddriving rotor and a corrugated faced driven rotor adapted to rotate uponan axis oblique to the axis of said driving rotor, a compression spacedefining flexible element of corrugated form interconnecting said rotorsand means to rotate said driving rotor whereby said flexible element isreversingly flexed by said rotors for the displacement of an entrainedfluid.

19. In rotary fluid displacement devices the combination of a fixedhousing, a pair of circumferentially corrugated conic rotors, journalscarried by said housing arranged for the rotation of said rotors onseparate but intersecting axes, and flexible corrugated means disposedbetween and interconnecting said rotors to form displacementcompartments in cooperation with said rotors.

20. In a rotary fluid displacement device comprising a fixed housing, apair of circumferentially corrugated conic rotors and journals carriedby said housing arranged for the rotation of said rotors on separate butintersecting axes, the improvement comprising flexible corrugated meansdisposed between and interconnecting said rotors arranged to formdisplacement compartments in cooperation with said rotors.

21. A rotary displacement device comprising a driving rotor, a drivenrotor adapted to rotate upon an axis oblique to the axis of said drivingrotor, compression space defining means of circumferentially corrugatedflexible material interconnecting said rotors and means to rotate saiddriving rotor whereby said compression space defining means isreversingly flexed for displacement of an entrained fluid.

22. A rotary displacement device comprising a driving rotor, a drivenrotor arranged for rotation upon an axis oblique to the axis of saiddriving rotor, a relatively thin rigid circumferentially corrugatedelement spaced from and disposed intermediate said rotors and chamberdefining means interconnecting said intermediate element and each saidrotor arranged to form radially extending expansible chambers uponrotation of said driving rotors.

23. A rotary displacement device comprising a driving rotor, an opposeddriven rotor adapted for rotation on an axis inclined to the axis of thesaid driving rotor, radially extending projections on the opposed workfaces of said rotors in a staggered relationship with respect to eachother, an annular disc spaced from and disposed between the work facesof said rotors, said disc formed with circumferential corrugationsprovidin radially extending projections centrally disposed between theadjacent radially extending projections on said rotor working faces and7.; flexible means disposed between and connected absa-ua .15 to eachsaid rote: and said centrally disposed Number \dise defining radiallyextending expansible 13 11512 chambers betweensaid rotors. 1,673,0492,324,168 JAMES M. CLARK.

REFERENCES CITED Number The following references are of record in thenle of thls patent: 687:022

UNITED STATES PATENTS 10 Number Name Date 32,372 Jones et a1. May 21,1861 Name Date Kirby July 2'7, 1920 Kearney July 24, 1928 Monteli usJuly 13, 1943 FOREIGN PATENTS Country Date Great Britain 1910 GreatBritain Jan. 30, 1919 Germany Jan. 20, 1940

